US11835096B2 - Plunging type constant velocity universal joint for propeller shaft - Google Patents

Plunging type constant velocity universal joint for propeller shaft Download PDF

Info

Publication number
US11835096B2
US11835096B2 US17/045,277 US201917045277A US11835096B2 US 11835096 B2 US11835096 B2 US 11835096B2 US 201917045277 A US201917045277 A US 201917045277A US 11835096 B2 US11835096 B2 US 11835096B2
Authority
US
United States
Prior art keywords
joint member
constant velocity
velocity universal
type constant
cage
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active, expires
Application number
US17/045,277
Other languages
English (en)
Other versions
US20210172481A1 (en
Inventor
Masazumi Kobayashi
Tomoshige Kobayashi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2018082974A external-priority patent/JP7382706B2/ja
Priority claimed from JP2018082972A external-priority patent/JP7382705B2/ja
Priority claimed from JP2018082973A external-priority patent/JP7246139B2/ja
Priority claimed from JP2018082977A external-priority patent/JP7437868B2/ja
Application filed by NTN Corp filed Critical NTN Corp
Assigned to NTN CORPORATION reassignment NTN CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KOBAYASHI, MASAZUMI, KOBAYASHI, TOMOSHIGE
Publication of US20210172481A1 publication Critical patent/US20210172481A1/en
Application granted granted Critical
Publication of US11835096B2 publication Critical patent/US11835096B2/en
Active legal-status Critical Current
Adjusted expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D3/224—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere
    • F16D3/2245—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere where the groove centres are offset from the joint centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D3/224—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D3/226—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a cylinder co-axial with the respective coupling part
    • F16D3/227—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a cylinder co-axial with the respective coupling part the joints being telescopic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22303—Details of ball cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22316—Means for fastening or attaching the bellows or gaiters
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S464/00—Rotary shafts, gudgeons, housings, and flexible couplings for rotary shafts
    • Y10S464/904—Homokinetic coupling
    • Y10S464/906—Torque transmitted via radially spaced balls

Definitions

  • the present invention relates to a plunging type constant velocity universal joint dedicated to propeller shafts.
  • Plunging type constant velocity universal joints capable of axial displacement and angular displacement are used for propeller shafts used in automobiles such as four-wheel drive vehicles (4WD vehicles) and front-engine, rear-wheel drive vehicles (FR vehicles).
  • the plunging type constant velocity universal joints include a double-offset plunging type constant velocity universal joint (DOJ), a tripod plunging type constant velocity universal joint (TJ), a cross-groove plunging type constant velocity universal joint (LJ), etc.
  • DOJ double-offset plunging type constant velocity universal joint
  • TJ tripod plunging type constant velocity universal joint
  • LJ cross-groove plunging type constant velocity universal joint
  • the propeller shafts are required to be smaller and lighter.
  • components such as an outer joint member, an inner joint member, and a cage
  • plunging type constant velocity universal joints for drive shafts have been directly used for plunging type constant velocity universal joints for propeller shafts except for a modified shape of the attachment portion of the outer joint member.
  • the plunging type constant velocity universal joints used for propeller shafts include a double-offset plunging type constant velocity universal joint (hereinafter also referred to as DOJ).
  • DOJ double-offset plunging type constant velocity universal joint
  • Patent Literature 1 JP H10-73129 A
  • the DOJ can slide a relatively large distance in the axial direction, has a good track record of use and stable performance, and further, can be designed to have eight balls to achieve size reduction and weight reduction.
  • the present inventors have studied various existing DOJs used for propeller shafts in order to meet the demands for further improvement in fuel efficiency of automobiles and size reduction, weight reduction, and increase in rotation speed of propeller shafts.
  • the present inventors have conducted various studies in order to achieve the above-mentioned objective and arrived at the present invention based on the following findings and ideas.
  • An existing 8-ball type DOJ for propeller shafts as shown in FIGS. 11 A, 11 B, and 12 has a maximum operating angle of about 25° so that it can also be used for drive shafts.
  • the present inventors have focused on the fact that the function of the DOJ can be limited by specializing the DOJ to required characteristics for use with propeller shafts. Specifically, it has been found that by making the DOJ dedicated to propeller shafts, the maximum operating angle can be limited to a low value (e.g., 15° or less), and size reduction and weight reduction of the DOJ can thereby be achieved.
  • the present invention is a plunging type constant velocity universal joint for a propeller shaft, including: an outer joint member having eight straight track grooves formed along an axial direction on a cylindrical inner surface; an inner joint member having eight straight track grooves formed along the axial direction on a spherical outer surface and opposing the straight track grooves of the outer joint member and a connecting hole in which female splines are formed; eight torque transmitting balls disposed between the straight track grooves of the outer joint member and the straight track grooves of the inner joint member; a cage having pockets accommodating the torque transmitting balls, a spherical outer surface guided in contact with the cylindrical inner surface of the outer joint member, and a spherical inner surface guided in contact with the spherical outer surface of the inner joint member, and is characterized in that a center of curvature of the spherical outer surface and a center of curvature of the spherical inner surface of the cage each have an equal and
  • the maximum operating angle of the above plunging type constant velocity universal joint for the propeller shaft By setting the maximum operating angle of the above plunging type constant velocity universal joint for the propeller shaft to 15° or less to specialize it to the required function for use with propeller shafts, the function of the plunging type constant velocity universal joint can be limited. And the size reduction and weight reduction of the plunging type constant velocity universal joint can be achieved.
  • the present invention is a plunging type constant velocity universal joint for a propeller shaft including: an outer joint member having eight straight track grooves formed along an axial direction on a cylindrical inner surface; an inner joint member having eight straight track grooves formed along the axial direction on a spherical outer surface and opposing the straight track grooves of the outer joint member and a connecting hole in which female splines are formed; eight torque transmitting balls disposed between the straight track grooves of the outer joint member and the straight track grooves of the inner joint member; a cage having pockets accommodating the torque transmitting balls, a spherical outer surface guided in contact with the cylindrical inner surface of the outer joint member, and a spherical inner surface guided in contact with the spherical outer surface of the inner joint member, and is characterized in that a center of curvature of the spherical outer surface and a center of curvature of the spherical inner surface of the cage each have an equal
  • the DOJ dedicated to propeller shafts, it is possible to limit the maximum operating angle to a low value, so that the maximum load applied to one ball is reduced. Accordingly, the load applied to the inner joint member and the outer joint member from the balls is reduced, and it is thus possible to reduce their wall thickness and achieve the axial size reduction and weight reduction of the DOJ.
  • the maximum operating angle of the DOJ to a low value, the amount of circumferential movement of the balls in the pockets of the cage is reduced, and it is thus possible to shorten the circumferential length of the pockets.
  • the center of curvature of the spherical outer surface of the cage and the center of curvature of the spherical inner surface of the cage are axially offset to maintain the balls on the bisector plane of the operating angle at any operating angle, so that the constant-speed torque transmission is achieved. Since the propeller shaft DOJ has a small and substantially constant operating angle, smooth torque transmission can be achieved even if the offset (f) between the center of curvature of the outer surface and the center of curvature of the inner surface of the cage is reduced.
  • the present inventors have found that by reducing the offset (f) of the cage, it is possible to reduce the axial dimension and radial wall thickness of the cage without impairing the function and durability of the DOJ, and have thereby achieved further size and weight reduction of the DOJ. Further, by reducing the offset (f) of the cage, the force acting on the pockets of the cage and the inner surface of the outer joint member is reduced, so that the heat generation of the DOJ for propeller shafts, which is used at high rotation speed, can be suppressed.
  • the present invention is a plunging type constant velocity universal joint for a propeller shaft including: an outer joint member having eight straight track grooves formed along an axial direction on a cylindrical inner surface; an inner joint member having eight straight track grooves formed along the axial direction on a spherical outer surface and opposing the straight track grooves of the outer joint member and a connecting hole in which female splines are formed; eight torque transmitting balls disposed between the straight track grooves of the outer joint member and the straight track grooves of the inner joint member; a cage having pockets accommodating the torque transmitting balls, a spherical outer surface guided in contact with the cylindrical inner surface of the outer joint member, and a spherical inner surface guided in contact with the spherical outer surface of the inner joint member, and is characterized in that a center of curvature of the spherical outer surface and a center of curvature of the spherical inner surface of the cage each have an equal
  • the DOJ dedicated to propeller shafts, it is possible to limit the maximum operating angle to a low value, so that the amount of axial movement of the balls relative to the inner joint member is reduced. Accordingly, it is possible to reduce the axial length of the track grooves of the inner joint member and hence the axial width Wi of the inner joint member, so that the axial size reduction and weight reduction of the DOJ can be achieved.
  • the maximum operating angle of the DOJ to a low value, the amount of circumferential movement of the balls in the pockets of the cage is reduced, and it is thus possible to shorten the circumferential length of the pockets.
  • the load applied to the axially opposing wall surfaces of the pockets of the cage is reduced, and it is thus possible to reduce the axial widths of the portions of the cage to which axial load is applied from the balls (specifically, the annular portions provided on both axial sides of the pockets). In this manner, the axial width of the cage is reduced, and further axial size reduction and weight reduction of the DOJ can be achieved.
  • the present invention is a plunging type constant velocity universal joint for a propeller shaft including: an outer joint member having eight straight track grooves formed along an axial direction on a cylindrical inner surface; an inner joint member having eight straight track grooves formed along the axial direction on a spherical outer surface and opposing the straight track grooves of the outer joint member and a connecting hole in which female splines are formed; eight torque transmitting balls disposed between the straight track grooves of the outer joint member and the straight track grooves of the inner joint member; a cage having pockets accommodating the torque transmitting balls, a spherical outer surface guided in contact with the cylindrical inner surface of the outer joint member, and a spherical inner surface guided in contact with the spherical outer surface of the inner joint member, and is characterized in that a center of curvature of the spherical outer surface and a center of curvature of the spherical inner surface of the cage each have an equal
  • the DOJ dedicated to propeller shafts, it is possible to limit the maximum operating angle to a low value, so that the maximum load applied to one ball is reduced. Accordingly, the load applied to the inner joint member and the outer joint member from the balls is reduced, and it is thus possible to reduce their wall thickness and achieve the axial size reduction and weight reduction of the DOJ.
  • the maximum operating angle of the DOJ to a low value, the amount of circumferential movement of the balls in the pockets of the cage is reduced, and it is thus possible to shorten the circumferential length of the pockets.
  • a plunging type constant velocity universal joint dedicated to propeller shafts that has a reduced size and weight, is qualitatively different from conventional one, and can contribute to the demands for further improvement in fuel efficiency of automobiles and increase in rotation speed of propeller shafts.
  • FIG. 1 is a diagram showing a propeller shaft equipped with a plunging type constant velocity universal joint for a propeller shaft according to an embodiment of the present invention.
  • FIG. 2 A is a longitudinal sectional view taken along line B-N-B in FIG. 2 B , showing a plunging type constant velocity universal joint for a propeller shaft according to an embodiment of the present invention.
  • FIG. 2 B is a cross sectional view taken along line A-A in FIG. 2 A .
  • FIG. 3 A is a diagram showing on the upper side a longitudinal section of the upper half of the plunging type constant velocity universal joint of FIG. 2 A with respect to axis line N-N, and on the lower side a longitudinal section of the upper half of the plunging type constant velocity universal joint of FIG. 11 A with respect to axis line N-N in a reversed orientation.
  • FIG. 3 B is a diagram showing on the upper side a longitudinal section of the lower half of the plunging type constant velocity universal joint of FIG. 2 A with respect to axis line N-N in a reversed orientation, and on the lower side a longitudinal section of the lower half of the plunging type constant velocity universal joint of FIG. 11 A with respect to axis line N-N.
  • FIG. 4 is a sectional view of the plunging type constant velocity universal joint of FIG. 2 A (upper half) and the plunging type constant velocity universal joint of FIG. 11 A (lower half), comparing them with regard to the axial movement of an inner joint member and a ball.
  • FIG. 5 is a longitudinal sectional view showing the inner joint member, cage, and ball of FIG. 2 A at an enlarged scale.
  • FIG. 6 A is an enlarged view of portion C of FIG. 5 .
  • FIG. 6 B is an enlarged view of portion D of FIG. 5 .
  • FIG. 7 A is a longitudinal sectional view showing an inner joint member, a cage, and a ball in a standard design in which a pocket clearance ⁇ 1 and an axial clearance ⁇ 2 are not provided.
  • FIG. 7 B is a longitudinal sectional view showing an inner joint member, a cage, and a ball in a design in which the pocket clearance ⁇ 1 and the axial clearance ⁇ 2 are provided.
  • FIG. 7 C is a longitudinal sectional view showing an inner joint member, a cage, and a ball in another design in which the pocket clearance ⁇ 1 and the axial clearance ⁇ 2 are provided.
  • FIG. 8 is a longitudinal sectional view showing the maximum operating angle of the plunging type constant velocity universal joint of FIGS. 2 A and 2 B .
  • FIG. 9 is a longitudinal sectional view showing an operating angle that can be taken by the plunging type constant velocity universal joint of FIGS. 2 A and 2 B when equipped with a boot.
  • FIG. 10 is a diagram comparing the cross section of the plunging type constant velocity universal joint in FIG. 2 B and the cross section of the plunging type constant velocity universal joint in FIG. 11 B .
  • FIG. 11 A is a longitudinal sectional view taken along line F-N-F in FIG. 11 B , showing an existing plunging type constant velocity universal joint.
  • FIG. 11 B is a cross sectional view taken along line E-E in FIG. 11 A .
  • FIG. 12 is a longitudinal sectional view showing the plunging type constant velocity universal joint of FIG. 11 when assembled.
  • FIG. 13 is a plan view showing an outline of the drive system of an FF-based 4WD vehicle.
  • FIG. 14 is a plan view showing an outline of the drive system of an FR-based 4WD vehicle.
  • the driving force is transmitted in the order of an engine 100 , a transaxle 113 , a differential 111 , a transfer 112 , a propeller shaft (rear propeller shaft) 102 , a differential 103 , drive shafts 104 , and rear wheels 105 .
  • the driving force is transmitted in the order of the engine 100 , the transaxle 113 , the differential 111 , drive shafts 109 , and front wheels 110 .
  • the driving force is transmitted in the order of an engine 100 , a transmission 101 , a propeller shaft (rear propeller shaft) 102 , a differential 103 , drive shafts 104 , and rear wheels 105 . Also, on the front side, the driving force is transmitted in the order of the engine 100 , the transmission 101 , a transfer 106 , a propeller shaft (front propeller shaft) 107 , a differential 108 , drive shafts 109 , and front wheels 110 .
  • constant velocity universal joints 45 , 46 , and 47 used for the drive shafts 104 and 109 placed after the differentials 103 , 108 , and 111 , which are final reduction gears have a maximum rotational speed of about 2000 min ⁇ 1 and a normal maximum operating angle of about 15°.
  • the operating angles of the constant velocity universal joints 45 , 46 , and 47 used for the drive shafts 104 and 109 are required to follow the vertical movement of the wheels 105 and 110 , and constantly fluctuate.
  • the fixed type constant velocity universal joints 46 attached to the front wheels 110 require large operating angles for steering.
  • the fixed type constant velocity universal joints 46 attached to the front wheels 110 have a maximum operating angle of about 45°
  • the other constant velocity universal joints 45 and 47 have a maximum operating angle of about 20 to 25°.
  • the propeller shafts 102 and 107 are arranged before the differentials 103 , 108 and 111 , which are final reduction gears, and are thus used at high rotation speed.
  • the maximum rotation speed is about 8000 min ⁇ 1 .
  • the differentials 103 , 108 , and 111 are mounted on the vehicle body side, and the propeller shafts 102 and 107 have large total lengths, a constant velocity universal joint 1 used for the propeller shafts 102 and 107 has a small and substantially constant operating angle.
  • the constant velocity universal joint 1 has a normal maximum operating angle of 10° or less and a maximum operating angle of about 15°.
  • the transmission torque of the constant velocity universal joint 1 used for the propeller shafts 102 and 107 is much smaller than that of the constant velocity universal joints 45 , 46 , and 47 used for the drive shafts 104 and 109 .
  • FIGS. 13 and 14 illustrates an example in which universal joints 43 , 44 , 48 , and 49 used for the propeller shafts 102 and 107 are cross joints, constant velocity universal joints may be used as at least one of these universal joints 43 , 44 , 48 , and 49 .
  • the propeller shaft 102 is composed of a first propeller shaft 41 located on the front side (the right side in the figure, the engine 100 side in FIG. 13 ) and a second propeller shaft 42 located on the rear side (the left side in the figure, the differential 103 side in FIG. 13 ).
  • the first propeller shaft 41 has a main part composed of a hollow pipe 64 and one end (front end) connected to the output side (the transfer 112 , see FIG. 13 ) of the engine 100 via the cross joint 43 .
  • the plunging type constant velocity universal joint 1 is connected to the other end (rear end) of the hollow pipe 64 of the first propeller shaft 41 .
  • the plunging type constant velocity universal joint 1 is the plunging type constant velocity universal joint for the propeller shaft according to the present embodiment.
  • the second propeller shaft 42 has a main part composed of a hollow pipe 65 and one end (front end) rotatably supported by a bearing support 60 .
  • the bearing support 60 consists of a bracket 61 , an elastic member 62 , and a rolling bearing 63 .
  • An outer ring 62 a of the elastic member 62 is fitted to the bracket 61
  • an inner ring 62 b of the elastic member 62 is fitted to the rolling bearing 63 .
  • a shaft 20 is provided at one end of the second propeller shaft 42 , and the outer periphery of the shaft 20 is fitted to the rolling bearing 63 and elastically supported in the radial direction.
  • One end (front end) of the shaft 20 is connected to a connecting hole of an inner joint member of the plunging type constant velocity universal joint 1 .
  • the other end (rear end) of the second propeller shaft 42 is connected to the differential 103 (see FIG. 13 ) via the cross joint 44 .
  • the first propeller shaft 41 and the second propeller shaft 42 are connected in the axial direction.
  • the plunging type constant velocity universal joint 1 for the propeller shaft (hereinafter also simply referred to as a plunging type constant velocity universal joint 1 ) according to the present embodiment is a so-called double-offset plunging type constant velocity universal joint (hereinafter also referred to as DOJ), and mainly includes an outer joint member 2 , an inner joint member 3 , torque transmitting balls 4 , and a cage 5 .
  • Eight straight track grooves 7 are formed on a cylindrical inner surface 6 of the outer joint member 2 at equal intervals in the circumferential direction and along the axial direction.
  • Eight straight track grooves 9 opposing the track grooves 7 of the outer joint member 2 are formed on a spherical outer surface 8 of the inner joint member 3 at equal intervals in the circumferential direction and along the axial direction.
  • the torque transmitting balls (hereinafter also simply referred to as balls) 4 are individually disposed between the straight track grooves 7 of the outer joint member 2 and the straight track grooves 9 of the inner joint member 3 .
  • the balls 4 are accommodated in pockets 5 a of the cage 5 .
  • the cage 5 has a spherical outer surface 12 and a spherical inner surface 13 , the spherical outer surface 12 is fitted to and guided in contact with the cylindrical inner surface 6 of the outer joint member 2 , and the spherical inner surface 13 is fitted to and guided in contact with the spherical outer surface 8 of the inner joint member 3 .
  • the spherical outer surface 12 of the cage 5 has a center of curvature O 1
  • the spherical inner surface 13 has a center of curvature O 2 .
  • the centers of curvature O 1 and O 2 have equal and axially opposite offsets f with respect to a center O 3 of the pockets 5 a of the cage 5 .
  • the center O 3 of the pockets 5 a refers to the intersection point of the plane including the respective axial direction-centers of the eight pockets 5 a and joint axis line N-N.
  • a large diameter portion 2 a joined to the hollow pipe 64 of the first propeller shaft 41 is formed at one end (right end in FIG. 2 A ) of the outer joint member 2 , and a seal cover 16 is attached to an inner hole near the large diameter portion 2 a .
  • Female splines (including serrations) 11 are formed in a connecting hole 10 passing through the axial center of the inner joint member 3 , and male splines 21 of the shaft 20 (see FIGS. 1 and 8 ) are fitted and connected thereto and fixed in the axial direction by a retaining ring 22 .
  • a retaining ring groove 14 is provided on the inner periphery of the other end (opening-side end) of the outer joint member 2 .
  • a retaining ring 23 (see FIG. 8 ) mounted in the retaining ring groove 14 prevents an inner assembly consisting of the inner joint member 3 , the balls 4 , and the cage 5 from coming out from the opening-side end of the outer joint member 2 .
  • a cylindrical surface-shaped notch 5 c for disposing the inner joint member 3 is provided on the inner periphery of the large-diameter-side end (right end in FIG. 2 A ) of the cage 5 .
  • a boot mounting groove 15 is provided on the outer periphery of the opening-side end of the outer joint member 2 . As shown in FIG.
  • a boot 25 is mounted in the boot mounting groove 15 of the outer joint member 2 and a boot mounting groove 20 a of the shaft 20 , and is tightened and fixed with boot bands 27 and 26 .
  • the boot 25 and the seal cover 16 function together to prevent the grease sealed inside the joint from leaking out and foreign matter from entering from outside the joint.
  • the overall structure of the plunging type constant velocity universal joint 1 of the present embodiment is as described above. Next, characteristic arrangements will be described. The findings and ideas in the development process leading to the characteristic arrangements of the plunging type constant velocity universal joint 1 of the present embodiment are as follows.
  • the double-offset plunging type constant velocity universal joint (DOJ) can slide a relatively large distance in the axial direction, have a good track record of use and stable performance, and further, can be designed to have eight balls to achieve size reduction and weight reduction. Focusing on these points, various DOJs used for the existing propeller shafts as shown in FIGS. 11 and 12 have been studied in order to meet the demands for further improvement in fuel efficiency of automobiles and size reduction, weight reduction, and increase in rotation speed of propeller shafts. As a result, the focus has been put on the fact that although the existing DOJs have a maximum operating angle of about 25° so that they can also be used for drive shafts, the function of the DOJ can be limited by specializing it to required characteristics for use with propeller shafts. Specifically, it has been found that by making the DOJ dedicated to propeller shafts, the maximum operating angle can be limited to a low value (e.g., 15° or less), and size reduction and weight reduction of the DOJ can thereby be achieved.
  • an existing plunging type constant velocity universal joint 201 is a double-offset plunging type constant velocity universal joint using eight torque transmitting balls 204 , mainly includes an outer joint member 202 , an inner joint member 203 , the torque transmitting balls 204 , and a cage 205 , and has a maximum operating angle of about 25°.
  • a diameter Db of the torque transmitting balls 4 of the plunging type constant velocity universal joint 1 according to the present embodiment is equal to a diameter Db′ of the torque transmitting balls 204 of the existing plunging type constant velocity universal joint 201 .
  • the basic internal arrangement is the same as that of the plunging type constant velocity universal joint 1 for the propeller shaft of the present embodiment, and portions having the same functions as those of the plunging type constant velocity universal joint 1 for the propeller shaft of the present embodiment are provided with reference numerals obtained by adding 200 to the reference numerals given in the present embodiment, and the center of the pockets, the centers of curvature, the offsets, and the like are provided with the alphabet reference characters obtained by adding a prime (′) to the characters of the present embodiment.
  • FIG. 3 A is a diagram showing on the upper side a longitudinal section of the upper half of FIG. 2 A with respect to axis line N-N, and on the lower side a longitudinal section of the upper half of FIG. 11 A with respect to axis line N-N in a reversed orientation.
  • FIG. 3 B is a diagram showing on the upper side a longitudinal section of the lower half of FIG. 2 A with respect to axis line N-N in a reversed orientation, and on the lower side a longitudinal section of the lower half of FIG. 11 A with respect to axis line N-N.
  • the cylindrical inner surface 6 of the outer joint member 2 and the conical stopper surface 5 d of the outer periphery of the cage 5 abut, so that the maximum operating angle is limited.
  • the maximum operating angle has the above meaning.
  • the maximum operating angle of the existing plunging type constant velocity universal joint 201 shown on the lower side of joint axis line N-N in FIG. 3 B is set to about 25° so that it can be used for drive shafts, and an inclination angle ⁇ ′ of a conical stopper surface 205 d of the outer surface of the cage 205 is formed at 12.5°, which is 1 ⁇ 2 of the maximum operating angle of 25°.
  • a wall thickness To of the outer joint member 2 (specifically, the radial distance between the groove bottom of the track grooves 7 and the outer surface of the outer joint member 2 ) and a wall thickness Ti of the inner joint member 3 (specifically, the radial distance between the groove bottom of the track grooves 9 and the pitch circle of the female splines 11 of the inner joint member 3 ) of the plunging type constant velocity universal joint 1 in the present embodiment are thinner than a wall thickness To′ of the outer joint member 202 and a wall thickness Ti′ of the inner joint member 203 of the existing plunging type constant velocity universal joint 201 , respectively.
  • the ratio Ti/Db between the wall thickness Ti of the inner joint member 3 and the ball diameter Db is 0.30 to 0.45. Also, the ratio To/Db between the wall thickness To of the outer joint member 2 and the ball diameter Db is 0.25 to 0.29.
  • the outer diameter of the cage 205 is increased, and it has not been possible to achieve sufficient size reduction of the plunging type constant velocity universal joint 201 . Accordingly, the wall thickness Ti′ of the inner joint member 203 has been unnecessarily large.
  • the amount of circumferential movement of the balls 4 in the pockets 5 a of the cage 5 is reduced, and it is thus possible to shorten the circumferential length of the pocket 5 a , which enables the reduction of the diameter of the cage 5 and hence the radial size reduction of the plunging type constant velocity universal joint 1 .
  • the diameter of the cage 5 it is possible to optimize the wall thickness of the inner joint member 3 and reduce the pitch circle diameter PCD BALL of the balls 4 . Accordingly, an outer diameter Do of the outer joint member 2 can be reduced.
  • the ratio PCD BALL /Db between the pitch circle diameter PCD BALL of the ball 4 and the diameter Db of the balls 4 is 3.3 or more and 3.6 or less.
  • FIG. 10 shows in comparison the respective cross sections of the plunging type constant velocity universal joint 1 of the present embodiment and the existing plunging type constant velocity universal joint 201 .
  • the plunging type constant velocity universal joint 1 of the present embodiment has achieved a size reduction of 5% or more in the outer diameter Do of the outer joint member 2 over the existing plunging type constant velocity universal joint 201 .
  • the optimum value of the ratio Do/Db between the outer diameter Do of the outer joint member 2 and the diameter Db of the balls 4 is 2.7 or more and 3.0 or less.
  • the maximum operating angle of the plunging type constant velocity universal joint 1 is a low value as described above, allowance can be made for the strength of the inner joint member 3 , and it is possible to increase the strength of the shaft 20 , which is the weakest part at a low operating angle. That is, it is possible to increase the pitch circle diameter (PCD SPL ) of the female splines 11 of the inner joint member 3 , and as a result, the strength of the propeller shaft at a low operating angle can be improved.
  • the ratio PCD SPL /Db between the pitch circle diameter PCD SPL of the female splines 11 and the diameter Db of the balls 4 is 1.75 or more and 1.85 or less.
  • an axial width Wi of the inner joint member 3 and an axial width Wc of the cage 5 of the plunging type constant velocity universal joint 1 are significantly reduced as compared to an axial width Wi′ of the inner joint member 203 and an axial width Wc′ of the cage 205 of the existing plunging type constant velocity universal joint 201 .
  • FIG. 4 is a diagram comparing the plunging type constant velocity universal joint 1 according to the present embodiment and the existing plunging type constant velocity universal joint 201 used for propeller shafts with regard to the axial movement between the inner joint member and the balls.
  • the amount of axial movement of the ball 4 of the plunging type constant velocity universal joint 1 is Zi
  • the amount of axial movement of the ball 204 of the existing plunging type constant velocity universal joint 201 is Zi′.
  • the amount of axial movement Zi is shorter than the amount of axial movement Zi′ because of the lower maximum operating angle. Since the axial width Wi of the inner joint member 3 and the axial width Wi′ of the inner joint member 203 are set in accordance with the respective amounts of axial movement Zi and Zi′, the axial width Wi of the inner joint member 3 of the plunging type constant velocity universal joint 1 is significantly reduced as compared to the axial width Wi′ of the inner joint member 203 of the existing plunging type constant velocity universal joint 201 .
  • the ratio Wi/Db between the axial width Wi of the inner joint member 3 and the ball diameter Db is 1.2 to 1.4.
  • the ball load applied to the pockets 5 a of the cage 5 is reduced.
  • This can reduce the axial wall thickness between the axially opposing wall surfaces of the pockets 5 a and the end surfaces of the cage 5 (that is, the axial wall thickness of the annular portions provided on both axial sides of the pockets 5 a ), leading to weight reduction.
  • the axial width We of the cage 5 of the plunging type constant velocity universal joint 1 is significantly reduced as compared to the axial width Wc′ of the cage 205 of the existing plunging type constant velocity universal joint 201 .
  • the ratio Wc/Db between the axial width Wc of the cage 5 and the ball diameter Db is 1.8 to 2.0.
  • the offset f of the cage 5 of the plunging type constant velocity universal joint 1 is set to be smaller than an offset f′ of the cage 205 of the existing plunging type constant velocity universal joint 201 .
  • the ratio f/PCD BALL between the offset f of the cage 5 and the pitch circle diameter PCD BALL of the balls 4 is set to be 0.07 or more and 0.09 or less.
  • the ratio f′/PCD BALL ′ between the offset f′ of the cage 205 of the existing plunging type constant velocity universal joint 201 and the pitch circle diameter PCD BALL ′ of the balls 204 is set to a value more than 0.09.
  • Table 1 shows dimensional ratios of the plunging type constant velocity universal joint 1 of the present embodiment and the existing plunging type constant velocity universal joint 201 .
  • PCD BALL Invented Product Existing Product Cage offset f/ball PCD 0.07-0.09 more than 0.09 Inner joint member wall thickness 0.30-0.45 more than 0.45 Ti/ball diameter Db Outer joint member wall thickness 0.25-0.29 more than 0.29 To/ball diameter Db Inner joint member width 1.2-1.4 1.6-1.8 Wi/ball diameter Db Cage width Wc/ball diameter Db 1.8-2.0 more than 2.0 Ball pitch circle diameter 3.3-3.6 more than 3.6 (PCD BALL )/ball diameter Db Spline pitch circle diameter 1.75-1.85 less than 1.75 (PCD SPL )/ball diameter Db Outer joint member outer diameter 2.7-3.0 more than 3.0 Do/spline PCD (PCD SPL )
  • an axial pocket clearance ⁇ 1 is provided between the axially opposing wall surfaces of the pocket 5 a of the cage 5 and the ball 4 .
  • an axial clearance ⁇ 2 is provided between the spherical inner surface 13 of the cage 5 and the spherical outer surface 8 of the inner joint member 3 .
  • the axial clearance ⁇ 2 is the amount of relative axial movement between the position where the spherical outer surface 8 of the inner joint member 3 abuts the spherical inner surface 13 of the cage 5 by moving the inner joint member 3 toward one side in the axial direction and the position where the spherical outer surface 8 of the inner joint member 3 abuts the spherical inner surface 13 of the cage 5 by moving the inner joint member 3 toward the other side in the axial direction, with the cage 5 fixed.
  • the sliding resistance of the plunging type constant velocity universal joint 1 is reduced, the vibration characteristics of the vehicle can be improved, and the improvement in life of the plunging type constant velocity universal joint 1 can be expected due to the effect of temperature reduction.
  • the use with propeller shafts is effective because they are used at a higher speed than drive shafts.
  • the pocket clearance ⁇ 1 is preferably set to 0 to 0.05 mm.
  • the pocket clearance ⁇ 1 can exhibit its effect even if it is small. If the pocket clearance ⁇ 1 is larger than 0.05 mm, the amount of deviation of the ball 4 from the bisector plane of the operating angle is increased, which may lead to decrease in the constant speed property and durability of the plunging type constant velocity universal joint 1 .
  • the axial clearance ⁇ 2 is preferably set to about 0.5 to 1.5 mm. If the axial clearance ⁇ 2 is smaller than 0.5 mm, the amount of vibration (axial amplitude) from the engine cannot be absorbed by the amount of relative axial movement between the inner joint member 3 and the cage 5 , and the vibration may be propagated. On the other hand, if the axial clearance ⁇ 2 is larger than 1.5 mm, the amount of deviation of the ball 4 from the bisector plane of the operating angle is increased, which may lead to decrease in the constant speed property and durability of the plunging type constant velocity universal joint 1 .
  • the axial pocket clearance ⁇ 1 is not provided between the axially opposing wall surfaces of the pocket 5 a of the cage 5 and the ball 4 .
  • a radius of curvature Rc of the spherical inner surface 13 of the cage 5 and a radius of curvature Ri of the spherical outer surface 8 of the inner joint member 3 although there is a slight spherical clearance for sliding guide, substantially Rc ⁇ Ri and no axial clearance ⁇ 2 is provided.
  • the plunging type constant velocity universal joint 1 has a design in which the pocket clearance ⁇ 1 and the axial clearance ⁇ 2 are provided (see FIG. 5 ) as shown in FIGS. 7 B and 7 C .
  • the pocket clearance ⁇ 1 is provided, and the radius of curvature Rc′ of the spherical inner surface 13 of the cage 5 is made larger than the radius of curvature Ri of the spherical outer surface 8 of the inner joint member 3 , and the center of curvature of the radius of curvature Rc′ is radially offset from the axial center of the cage 5 .
  • FIG. 7 C shows another design in which the pocket clearance ⁇ 1 and the axial clearance ⁇ 2 are provided.
  • the spherical outer surface 8 of the inner joint member 3 is formed of a single spherical surface having a radius of curvature Ri
  • the spherical inner surface 13 of the cage 5 has a cylindrical portion 13 a formed in area S at a position corresponding to the axial direction-center of the inner joint member 3 , and spherical surfaces having a radius of curvature Rc are smoothly connected to both ends of the cylindrical portion 13 a .

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Motor Power Transmission Devices (AREA)
  • Rolling Contact Bearings (AREA)
US17/045,277 2018-04-24 2019-04-12 Plunging type constant velocity universal joint for propeller shaft Active 2040-08-16 US11835096B2 (en)

Applications Claiming Priority (9)

Application Number Priority Date Filing Date Title
JP2018-082977 2018-04-24
JP2018082974A JP7382706B2 (ja) 2018-04-24 2018-04-24 プロペラシャフト用摺動式等速自在継手
JP2018-082973 2018-04-24
JP2018-082974 2018-04-24
JP2018082972A JP7382705B2 (ja) 2018-04-24 2018-04-24 プロペラシャフト用摺動式等速自在継手
JP2018-082972 2018-04-24
JP2018082973A JP7246139B2 (ja) 2018-04-24 2018-04-24 プロペラシャフト用摺動式等速自在継手
JP2018082977A JP7437868B2 (ja) 2018-04-24 2018-04-24 プロペラシャフト用摺動式等速自在継手
PCT/JP2019/016030 WO2019208277A1 (ja) 2018-04-24 2019-04-12 プロペラシャフト用摺動式等速自在継手

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2019/016030 A-371-Of-International WO2019208277A1 (ja) 2018-04-24 2019-04-12 プロペラシャフト用摺動式等速自在継手

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US18/383,285 Division US20240052893A1 (en) 2018-04-24 2023-10-24 Plunging type constant velocity universal joint for propeller shaft

Publications (2)

Publication Number Publication Date
US20210172481A1 US20210172481A1 (en) 2021-06-10
US11835096B2 true US11835096B2 (en) 2023-12-05

Family

ID=68295474

Family Applications (2)

Application Number Title Priority Date Filing Date
US17/045,277 Active 2040-08-16 US11835096B2 (en) 2018-04-24 2019-04-12 Plunging type constant velocity universal joint for propeller shaft
US18/383,285 Pending US20240052893A1 (en) 2018-04-24 2023-10-24 Plunging type constant velocity universal joint for propeller shaft

Family Applications After (1)

Application Number Title Priority Date Filing Date
US18/383,285 Pending US20240052893A1 (en) 2018-04-24 2023-10-24 Plunging type constant velocity universal joint for propeller shaft

Country Status (4)

Country Link
US (2) US11835096B2 (zh)
CN (1) CN112020613B (zh)
DE (1) DE112019002125T5 (zh)
WO (1) WO2019208277A1 (zh)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7292008B2 (ja) * 2017-03-17 2023-06-16 Ntn株式会社 後輪用ドライブシャフト専用の摺動式等速自在継手

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05306604A (ja) 1992-04-28 1993-11-19 Nippondenso Co Ltd 内燃機関のバルブタイミング調整装置
JPH1073129A (ja) 1996-06-28 1998-03-17 Ntn Corp 摺動型等速自在継手
JP2000314430A (ja) 1999-04-28 2000-11-14 Ntn Corp プロペラシャフト用摺動型等速自在継手
JP2007100797A (ja) 2005-10-03 2007-04-19 Ntn Corp 摺動式等速自在継手
JP2007224995A (ja) 2006-02-22 2007-09-06 Ntn Corp 等速ジョイント
US7431653B2 (en) * 2004-01-20 2008-10-07 Ntn Corporation Sliding type constant velocity universal joint
JP2009228813A (ja) 2008-03-24 2009-10-08 Ntn Corp 等速自在継手
JP2011052625A (ja) 2009-09-03 2011-03-17 Honda Motor Co Ltd 内燃機関の可変動弁装置
US9926985B2 (en) * 2013-08-09 2018-03-27 Hyundai Wia Corporation Sliding ball type constant velocity joint for vehicles

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4223358B2 (ja) * 2003-09-04 2009-02-12 Ｎｔｎ株式会社 固定式等速自在継手
JP2010249284A (ja) * 2009-04-20 2010-11-04 Ntn Corp 固定型等速自在継手
JP6114644B2 (ja) * 2013-06-26 2017-04-12 Ntn株式会社 固定式等速自在継手
JP6328452B2 (ja) * 2014-03-17 2018-05-23 Ntn株式会社 固定式等速自在継手
JP2017166579A (ja) * 2016-03-16 2017-09-21 Ntn株式会社 摺動式等速自在継手

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05306604A (ja) 1992-04-28 1993-11-19 Nippondenso Co Ltd 内燃機関のバルブタイミング調整装置
JPH1073129A (ja) 1996-06-28 1998-03-17 Ntn Corp 摺動型等速自在継手
US6299543B1 (en) 1996-06-28 2001-10-09 Ntn Corporation Plunging type constant velocity joint
JP2000314430A (ja) 1999-04-28 2000-11-14 Ntn Corp プロペラシャフト用摺動型等速自在継手
US6280338B1 (en) 1999-04-28 2001-08-28 Ntn Corporation Plunging constant velocity universal joint for propeller shaft
US7431653B2 (en) * 2004-01-20 2008-10-07 Ntn Corporation Sliding type constant velocity universal joint
JP2007100797A (ja) 2005-10-03 2007-04-19 Ntn Corp 摺動式等速自在継手
JP2007224995A (ja) 2006-02-22 2007-09-06 Ntn Corp 等速ジョイント
JP2009228813A (ja) 2008-03-24 2009-10-08 Ntn Corp 等速自在継手
JP2011052625A (ja) 2009-09-03 2011-03-17 Honda Motor Co Ltd 内燃機関の可変動弁装置
US9926985B2 (en) * 2013-08-09 2018-03-27 Hyundai Wia Corporation Sliding ball type constant velocity joint for vehicles

Non-Patent Citations (4)

* Cited by examiner, † Cited by third party
Title
Decision of Refusal dated Mar. 31, 2023 in corresponding Japanese Patent Application No. 2018-082977, with English-language translation.
International Preliminary Report on Patentability and Written Opinion of the International Searching Authority dated Oct. 27, 2020 in International (PCT) Application No. PCT/JP2019/016030.
International Search Report dated Jul. 2, 2019 in International (PCT) Application No. PCT/JP2019/016030.
Notice of Reasons for Refusal dated Sep. 27, 2022 in corresponding Japanese Patent Application No. 2019-049764, with English language translation.

Also Published As

Publication number Publication date
WO2019208277A8 (ja) 2020-10-29
CN112020613B (zh) 2023-11-14
WO2019208277A1 (ja) 2019-10-31
DE112019002125T5 (de) 2021-01-14
US20210172481A1 (en) 2021-06-10
CN112020613A (zh) 2020-12-01
US20240052893A1 (en) 2024-02-15

Similar Documents

Publication Publication Date Title
US8070611B2 (en) Plunging cross-track constant velocity joint
WO2005098253A1 (en) Boot with articulating and plunging convolutes
US20240052893A1 (en) Plunging type constant velocity universal joint for propeller shaft
EP1777079B1 (en) Wheel drive unit
US20040097292A1 (en) High angle constant velocity joint
US6766877B2 (en) Tear away bracket
JP7437868B2 (ja) プロペラシャフト用摺動式等速自在継手
US11353066B2 (en) Fixed type constant velocity universal joint for rear-wheel drive shaft
JP7382706B2 (ja) プロペラシャフト用摺動式等速自在継手
US6997813B2 (en) Rotary shaft
CN110431324B (zh) 用于后轮用驱动轴的滑动式等速万向联轴器
JP7382705B2 (ja) プロペラシャフト用摺動式等速自在継手
JP7246139B2 (ja) プロペラシャフト用摺動式等速自在継手
EP3597949A1 (en) Rear-wheel drive shaft
US11359676B2 (en) Fixed-type constant velocity universal joint
US20030171154A1 (en) Propeller shaft assembly
US11326649B2 (en) Rear-wheel drive shaft
JP7224107B2 (ja) 後輪用ドライブシャフト専用の摺動式等速自在継手
JP7292008B2 (ja) 後輪用ドライブシャフト専用の摺動式等速自在継手
WO2023026826A1 (ja) 摺動式等速自在継手
JP2002250359A (ja) 等速自在継手
US20030236123A1 (en) Rotary shaft
US20030234132A1 (en) Flexible propeller shaft coupling

Legal Events

Date Code Title Description
FEPP Fee payment procedure

Free format text: ENTITY STATUS SET TO UNDISCOUNTED (ORIGINAL EVENT CODE: BIG.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

AS Assignment

Owner name: NTN CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KOBAYASHI, MASAZUMI;KOBAYASHI, TOMOSHIGE;REEL/FRAME:055265/0991

Effective date: 20210204

STPP Information on status: patent application and granting procedure in general

Free format text: APPLICATION DISPATCHED FROM PREEXAM, NOT YET DOCKETED

STPP Information on status: patent application and granting procedure in general

Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION

STPP Information on status: patent application and granting procedure in general

Free format text: NON FINAL ACTION MAILED

STPP Information on status: patent application and granting procedure in general

Free format text: RESPONSE TO NON-FINAL OFFICE ACTION ENTERED AND FORWARDED TO EXAMINER

STPP Information on status: patent application and granting procedure in general

Free format text: NOTICE OF ALLOWANCE MAILED -- APPLICATION RECEIVED IN OFFICE OF PUBLICATIONS

STPP Information on status: patent application and granting procedure in general

Free format text: NOTICE OF ALLOWANCE MAILED -- APPLICATION RECEIVED IN OFFICE OF PUBLICATIONS

STPP Information on status: patent application and granting procedure in general

Free format text: PUBLICATIONS -- ISSUE FEE PAYMENT RECEIVED

STPP Information on status: patent application and granting procedure in general

Free format text: PUBLICATIONS -- ISSUE FEE PAYMENT VERIFIED

STCF Information on status: patent grant

Free format text: PATENTED CASE